Tens-transfer mechanism



Feb. 27, 1962 A. J. MALAvAzos ET AL 3,022,948

TENS-TRANSFER MEGHANISM Filed Nov. 2, 1959 y 4 Sheets-Sheet 1 Feb. 27, 1962 A. J. MALAvAzos ETAL 3,022,943

TENS-TRANSFER MECHANISM Filed Nov. 2, 1959 4 Sheets-Sheet 2 Feb. 27, 1962 A. J. MALAvAzos ETAL 3,022,948

TENS-TRANSFER MECHANISM 4 Sheets-Sheet 3 Filed NOV. 2, 1959 .ww um, h2 flu/(Mw Feb. 27, 1962 A. J. MALAvAzos ETAL 3,022,948

TENS-TRANSFER MECHANISM 4 Sheets-Sheet 4 Filed Nov. 2, 1959 GNN? United States Patent Oitice 3,022,948 Patented Feb. 2?, 1962 3,022,948 TENS-TRANSFER MECHANISM Arthur J. Malavazos, Hayward, and John W. Jamieson,

San Leandro, Calif., assignors to Friden, Inc., a corporation of California Filed Nov. 2, 1959, Ser. No. 850,153 Claims. (Cl. 23S-13S) rlhis invention relates to an improved auxiliary, or outboard, tens-transfer mechanism for a calculating machine of the rThomas-type, such as disclosed in U.S. Patent No. 2,229,889, issued to Carl M. F. Friden on January 28, 1941, and is an improvement of the tens-transfer mechanism disclosed in the copending application of Vito Viola et al., S.N. 850,184 liled November 2, 1959.

The device disclosed in the above-mentioned copending application of Vito Viola et al., comprises a shiftable accumulator, or register carriage, in which a plurality of ordinally arranged register wheels are mounted, certain of such wheels will be positioned to the right and/or left of the stationary portion of the machinevin any shiftable position of the carriage. Within the stationary portion of the machine, an ordinal selection mechanism, an actuating mechanism and a tens-transfer mechanism are located to eiect registrations of values in those register wheels aligned with the selection mechanism. In order to eifect la tens-transfer in the register Wheels positioned tothe left of the selection mechanism, an auxiliary tenstransfer mechanism is provided and comprises a series of ordinally arranged tens-transfer disks, associated with the register wheels located to the left of the selection mechanism. Furthermore, there is provided individual tenstransfer actuator hails for each of these register wheels, which hails are rockably and nonslidably mounted on a common shaft axially adjustable to either of two positions in accordance with the sign character of registrations in the register. These tens-transfer actuator bails can be rocked into notches provided in the tens-transfer disks and then axially adjusted to effect a simultaneous tenstransfer in all of the outboard order accumulator wheels provided in the register carriage. One particular disadvantage found in the Vito Viola et al. mechanism, and one which the present invention described herein is adapted to overcome, is that of the base, or bar, of the U-shaped tens-transfer actuator hails having a tendency to bend, especially those bails associated with the higher outboard orders, as they are rocked into active position.

t is, therefore, an object of the present invention to provide an improved auxiliary tens-transfer mechanism for calculating machines.

t is another object of the present invention to provide an improved independently operable tens-transfer actuator means in an auxiliary tens-transfer mechanism, for use in the shiftable carriage of a calculating machine.

Another object of the present invention is to provide individual tens-transfer drum actuators for each outboard order of a calculating machine. l

A further object of this invention is to provide means whereby the independently operable tens-transfer drum actua-tors associated with the outboard orders are successively disabled as they are ordinally shifted inboard of the stationary portion of the machine.

Still another object is to provide an improved auxiliary tens-transfer mechanism for a calculating machine, whereby incremental transfers into the outboard order accumulator wheels are controlled by the highest inboard order `accumulator wheel irrespective of the ordinally shifted position of the register carriage.

Still a further object of the present invention is to provide a means operable to disable the operation of the drum actuators of an improved auxiliary tens-transfer mechanism during a shifting operation of the accumulator, or register, carriage.

The invention, both as to its organization and method of operation, together with further objects and advantages thereof, will best be understood by referring to the following specitication taken in connection with the accompartying drawings, of which:

FIG. 1 is a top plan view of a calculating machine incorporating an outboard full-carry tens-transfer mechanism exemplifying the invention;

FIG. 2 is a stepped plan view of the conventional actuating and tens-transfer mechanism for the inboard orders of the machine, with the accumulator carriage and a portion of the selection and actuating mechanism in certain orders omitted to better illustrate the construction;

FIG. 3 is a partial cross-sectional elevational view showing the auxiliary tens-transfer drum actuators and the actuating mechanism therefor, the view being taken on the planes as indicated by the lines 3-3 of FIG. 1;

FIG. 4 is a sectional view of the tens-transfer drum actuators, as viewed from the left in FIG. 1, showing the relative angular displacement of the actuating portion thereof;

FIG. 5 is a fragmentary elevational view of the actuating arm blocking plate, the View being taken on a plane as indicated by line 5-5 of FIG. 3;

FIG. 6 is a View of the centralizer mechanism as viewed from the left in FIG. 3;

FIG. 7 is a front elevational view, showing the outboard order register wheels in the shiftable carriage and the auxiliary tens-transfer actuating mechanism therefor, the view being taken on the transverse planes, as indicated by the lines 7 7 of FIG. 3;

FIG. 8 is a fragmentary sectional plan view of the outboard portion of the accumulator register showing the tens-transfer disks and the ordinally disposed tens-transfer drum actuators therefor; and

FIG. 9 is an isometric view of a single tens-transfer drum actuator showing the construction thereof.

The invention to be described herein is preferably constructed in a calculating machine of the Thomas-type, such as that shown in the above-mentioned Friden Patent No. 2,229,889. It is not intended that its use should be limi-ted only to a machine of this construction, since it is evident that the underlying principles thereof may be advantageously applied to other types of calculating machines.

The mechanism which is conventional in the machine described in the above-mentioned patent will not be described herein unless necessary to provide a more cornplete understanding of the mechanism of the present invention. The calculating machine to which the invention is particularly adapted, generally includes a body in which the selecting, actuating and tens-transfer mechanisms are mounted, and a shiftable accumulator carriage, which also, among other things, supports a part of the tens-transfer mechanism.

In lthe preferred embodiment of the invention disclosed herein, the body of the calculating machine includes a base (not shown) having a cover 11 (FIG. 1) and right and left side frame members 12 and 13, respectively, mounted thereon (FIG. 2). Between the respective side frame members 12 and 13 there is provided a plurality of transverse frame members including a front bearing plate 14, a center bearing plate 15 and a rear bearing plate 16, all of which serve to support various parts of the operating mechanism referred to hereinafter.

The shiftable register carriage 20 (FIGS. 1, 3 and 7) is mounted in a Well-known manner for endwise shifting movement within the framework of the machine and is under the control of a conventional power-driven mechanism. The shifting of the carriage in either direction may be selectively controlled by the depression of one or the other of the pair of manually operable shift keys 17 and 17', or may be automatically controlled by certain function control mechanisms which are customarily provided in machines of this character.

Provided Within the carriage 2i) is a plurality of ordinally arranged accumulator numeral wheel shafts 21, which are suitably journalled in the carriage frame bar 22. At its upper end, each shaft 21 carries -a numeral wheel 23 having the digits from O to 9 inscribed thereon, and at its lower end carries a ten-tooth gear 24. Each numeral wheel 23 is rotatable in either direction to register positive or negative values and, for this purpose, gear 24 (FIGS. 2 and 3) has associated therewith a pair of opposed bevel gears 23 and 29 formed on the respective ends of spool 3G slidaoly and nonrotatably mounted on the square selection shaft 31. At its ends each square shaft 31 is suitably journalled in the front plate 14 and the rear plate 16 and intermediate its ends in plate 15. The spools 30 and associated gears 23 and 29 are shiftable in either direction, relative to the corresponding gears 24, by a transversely extending plus-minus gate strap 32 positioned between each pair of gears 28, 29 and supported at its ends by similar arms 33, which arms are secured on gate shaft 34 journalled for rocking movement in side frame members 12 and 13. Thus, if the gate 32 is rocked counter-clockwise (FIG. 3), the gears 28 will enmesh with the corresponding accumulator gears 24 to effect an additive registration on the numeral wheels 23. Conversely, if the gate is rocked clockwise, the gears 29 will enmesh with the corresponding accumulator gears 24 and a subtractive registration will be effected. The rocking of the gate 32 may be selectively controlled in a well-known manner by depression of the plus key 18 or minus key 19 (FlG. l).

lt can be seen from the above description that an increment of rotation of a spool 3ft will be transmitted to its associated accumulator wheel 23 following the engagement of either of the gears 28 or 29 with the corresponding gear 24. Means are provided in the various orders of the machine to determine the number of increments of such rotation. For this purpose, a plurality of numeral, or value, keys 3S is provided for each order of the machine (FIG. l). The numeral keys 38 in each order cooperate conventionally with a pair of differential value selection slides 39 and 4t) (FlG. 2) which are mounted for endwise shifting movement and are differentially set in accordance with the values of the depressed value keys. The ordinal selection slides 39 are associated with the numeral keys 33, determining Values from 6 to 9, while the slides 4i) are associated with the numeral keys 38, determining values from "1 to 5. At their rearward ends, the selection slides 39 and 4t) are operatively connected to a pair of selection gears 41 and 42, respectively, which gears are slidably but nonrotatably mounted on the square shafts 31. Each selection gear 41 and 42 is provided with ten teeth and is arranged to cooperate, respectively, with the teeth of the stepped toothed actuators 43 and 44. The square shafts 31 are ordinally arranged transversely of the machine in accordance with the ordinal arrangement of the keys 38 and the register wheels 23. For each adjacent pair of the transversely spaced orders o-f the selection mechanism, there is provided a single longitudinal actuator shaft 46 on which each pair of stepped tooth actuators 43 and 44 for the respective orders are secured. Accordingly, the square selection shafts 31 of each of the adjacent pair of orders are spaced to either side of, and above, the associated actuator shaft 46 (PEG. 2). At its forward end, each of the actuator shafts 46 is journalled in the transverse bearing plate 14, and at its rearward end is journalled in the auxiliary crossframe member 47 spaced from, and secured on, bearing plate 15. Adjacent the forward end thereof, each of the actuator shafts 46 carries a bevel gear 48 meshing with a similar bevel gear 49 secured on the main drive shaft S0, which extends transversely of the machine and is journalled in side frame members 12 and 13.

In the embodiment shown, a conventional source of power is provided in the form of an electric motor which serves, through a well-known cyclically operable clutch means, to impart one rotation to the main drive shaft 50 for each cycle of machine operation. Thus, for each rotation of the main drive shaft 5G, the actuator shafts 46, and hence the stepped tooth actuators 43 and 44, will receive a single rotation to cause registration of the value selected by the depressed value key, or keys, 38 in the associated accumulator register wheels 23. Each pair of stepped tooth actuators 43 and 44 is mounted in angularly offset relation on the corresponding actuator shaft 46 and also relative to the stepped tooth actuator associated with the adjacent orders. The arrangement is such that the teeth of the actuators 43 and 44 associated with the units order, i.e., the rightmost order in FIG. 2, first become active, followed by the teeth of the actuators 43 and 44 associated with the tens order and the other orders in succession thereafter.

Conventional means are provided for preventing overthrow of the numeral wheels upon termination of an actuation thereof. For this purpose, the stepped tooth actuators 43 and 44 of each pair of actuators are so positioned on the corresponding actuator shafts 46 that their last active teeth are in alignment and the Geneva wheel 55 (FIG. 2) carried by each square selection shaft 31 cooperates with the locking disk 56 on the associated actuator shaft 46. Each Geneva wheel S5 has ten concave faces, the actively positioned one of which is engaged by a high portion of the associated locking disk 56 immediately following actuation of either gear 41 or 42, by the last active tooth of the respective corresponding actuator 43 or 44. Consequently, the associated square shaft 31 and numeral wheel 23 are positively locked against further rotation. Since this mechanism forms no part of the present invention, the foregoing description is believed to suffice. However, for a more complete disclosure, reference is to be made to the afore-mentioned Patent No. 2,229,889.

Machines of the type presently being described are generally provided with six actuator shafts 46 and twelve square shafts 31. The rst ve actuator shafts 46 (from the right in FIG. 2) carry the stepped tooth actuators 43 and 44 cooperating with the respective pairs of adjacent shafts 31 associated with the ten orders of the selection mechanism to control the registration of a value in the keyboard in the register wheels 23. The leftmost actuator shaft 46 (FlG. 2) cooperates with the remaining pair of square shafts 31 to control a tens-transfer from the tenth order into the eleventh and twelfth orders of the accumulator register. Thus, the twelfth order numeral wheel 23, from the righthand end of the register carriage 20, is normally the highest order to receive a tens-transfer impulse from the conventional tens-transfer mechanism when the carriage is in its leftmost position. Hence, as stated hereinbefore, inasmuch as the conventional tens-transfer mechanism is mounted within the stationary portion of the machine and is contained in the space existing between the right and left side frames of the machine, the first twelve orders of the register may be considered to be the inboard orders thereof when the register carriage is in its leftmost position, whereas, all higher orders of the register may be considered to constitute the outboard orders of the register.

Generally, the tens-transfer mechanism associated with the selection mechanism cooperates with the actu` ator shafts 46 in a well-known manner and comprises tripping means associated with each numeral wheel, except the highest order wheel, enabled by a lower order wheel to effect a drive connection from a tens-transfer actuator to the numeral wheel of the next higher order. Thus, the next higher order numeral wheel receives one increment of rotation when the lower order numeral wheel passes from 9 to 0 or 0 to 9. The sign character of the transferred increment is determined in the same manner as the sign character of the digitation, i.e., by the meshing engagement of the gears 28 or 29 of spools 3i? with the corresponding gears 24.

To effect the tripping of a transfer, each numeral wheel shaft 21 (FIGS. 2 and 3) carries a single tooth tens-transfer cam 6ft positioned immediately below the carriage frame bar 22 for cooperation with the corresponding tens-transfer lever 61. Each of the tens-transfer, or tripping, levers 61 is secured on a stud 62, which studs are journalled in ordinally spaced bores (not shown) provided in the carriage frame bar Z2. Each tens-transfer lever 61 has a nose 63 positioned in the path of the corresponding transfer cam 6i), so that when the numeral Wheel 23 of a lower order passes from 9 to 0, or from to 9, the nose 63 is engaged by the cam 60 and the lever 61 is rocked, in a counter-clockwise direction as viewed in FIG. 2, the limit of such movement being determined by the operation of a conventional detent, not shown herein. Each lever 61 is also provided with an arm 64 extending into the next higher order of the machine and normally engaging the lever 61 of the next higher order adjacent its pivot stud 62. A formedover ear 66 at the extremity of each extended arm 64 (FIG. 2) lies between a pair of annular flanges 67 formed on hub 68 of the tens-transfer gear 69 slidably but nonrotatably mounted on the square shaft 31 in the adjacent higher order. Upon rocking movement (counter-clockwise in FIG. 2) of a tens-transfer lever 61 by the tens-transfer cam 69 of the corresponding numeral wheel 23, the hub 65 and gear 69 in the adjacent higher order is shifted forwardly of the machine to position the gear 69 in operative relation with respect to the single tooth tens-transfer actuator 71 therefor. rfhe single tooth tens-transfer actuators 71 for each pair of adjacent orders are spaced apart and secured on the corresponding locking disks 56 by suitable studs 73. From the above description it is seen that each time a tenstransfer is determined in one order of the machine, the tens-transfer gear 69 of the adjacent higher order is shifted into active position to be subsequently operated by the associated single tooth tens-transfer actuator 71.

Means are provided for resiliently maintaining the tenstransfer gears 69 in either shiftedposition thereof, and associated with the maintaining means is a restore cam which cooperates with the tens-transfer gears 69 of each pair of adjacent orders. The rearrnost annular flange 67 of each gear hub 66 extends between spaced annular flanges 7S on the corresponding stub shaft 79 which is slidably mounted in the crossb'ar 47 and auxiliary transerse member Sii. Each shaft 79 is provided with a pair of suitable spaced annular grooves for cooperation with a spring-urged ball detent mountedin the transverse member 80, all of which is conventional and is not shown herein. Thus, the stub shafts 79 and associated tenstransfer gears 69 are maintained resiliently in either theirrearward inoperative position or in their forward operative position. Referring to FIG. 2, when a tens-transfer gear 69 is shifted to the operative position, the forward end of,

the associated shaft 79 will project beyond the crossbar 47 into the path of the cam S1 integrally formed with, and arcuately offset from, the rearmost tens-transfer actuator 71 of each pair of associated tens-transfer actuators. As seen in FIG. 2, each pair of shafts 79 for the adjacent orders of the machine are spaced closer together than the spacing between the orders, so that the forward end of both shafts 7h of each pair lies in the path of the restoring cam 81 carried by the corresponding actuator shaft 46. The cams 81 are successively operable to restore each operatively positioned shaft 79 and associated gear 69 to the inoperative position thereof following a tens-transfer operation in the corresponding orders. v A similar tens-transfer actuator construction is provided for all orders including thetwo highest inboard orders, i.e., the eleventh and twelfth orders of the machine, thereby enabling a tens-transfer intothese orders.

6 It is to be noted in FIG. 2 that although there are two tens-transfer actuators 71 shown on the right-hand actuator shaft 46, only that actuator associated with the tenstransfer gear 69 in the tens order is necessary, since no tens-transfer occurs in the units order. It will also be noted that the single tooth on each of the tens-transfer actuators 71 on each actuator shaft 46, as well as the successive pairs of actuators 71 on the adjacent actuator shafts 46, are angularly displaced to provide for operation of the tens-transfer actuators seriatim from the lowest, or tens, order to the highest order.

Briefly, assuming that a tens-transfer has been determined by shifting two of the tens-transfer gears 69 in adjacent orders to an active position, the corresponding tens-transfer actuators 71 will have rotated from their fidi-cycle position to a position where the tooth of the rearward actuator 71 becomes effective to impart a onetenth rotation to the associated gear 69 to enter the transferred increment into the corresponding numeral wheel. Subsequently, the other, or forward, actuator 71 will become effective with respect to its associated tens-transfer gear 69 to cause a one-tenth rotation thereof and complete the tens-transfer into the associated numeral wheel. The forward actuator 71, in effect, trails the rearward actuator 71 a suflicient angular distance to accommodate the setting of the tens-transfer mechanism in the adjacent higher order by movement of the gear 69 to the active position, if a transferred increment entered in the adjacent lower order numeral wheel determines a tenstransfer operation into the next higher order numeral wheel.

In order to effect an incremental transfer from one order of the register to the next higher order thereof beyond the twelfth, or highest inboard, order numeral wheel 23, the machine shown in the accompanying drawings is provided with an auxiliary tens-transfer mechanism, which enables a tens-transfer operation to be effected throughout the entire capacity of the register.

Referring to FIGS. 3, 7 and 8, the register wheel shaft 211 in the twelfth order of the carriage 20, i.e., the twelfth shaft 21 from the right-hand end of the carriage, as well as each of the successive higher outboard order shafts 21, has secured thereto a tens-transfer gear disk 106. It will be recalled from the above description that the main, or conventional, tens-transfer mechanism is operable, with the carriage in its leftmost position, to effect an incremental transfer into the twelfth order accumulator wheel 23. As pointed out hereinafter, this twelfth order accumulator wheel becomes operative to extend the incremental transfer into the higher outboard orders of the register carriage 20, i.e., the thirteenth to the twentieth orders, inclusive. Against the upper surface of each of the tens-transfer gear disks 100, there is secured a backing disk 101 having a recess, or notch, 10?. (see FIG. 8) in its peripheral surface situated between the interdental teeth of the tens-transfer gear disk 100, which correspond to the ntunerals 0 and 9 provided on the numeral wheels 23.

ln order to couple one order of the outboard orders of the register wheels to the adjacent higher order, if a value entered in the adjacent lower order register wheel determines a tens-transfer into the next higher order, there is provided a series of independently rockable tens-transfer drum actuators, or cylindrical racks, 10S, 106, 167, 168, 109, 116, 111, 112 and 113 (FlGS. 3, 4, 7, 8 and 9) associated respectively with the tens-transfer gear disks 10G on the highest inhoard order dial shaft 21, i.e., the twelfth order dial shaft, and on each of the higher outboard order dial shafts (e.g., the thirteenth to the twentieth orders, inclusive) of the register carriage 2t). The tens-transfer drum actuators 19S to 113, inclusive,l are adjacently mounted in an ordinal arrangement on a common rod 116 supported at its ends for endwise movement in the respective depending arms, or flanges, of a stirrup 117. The drum actuators 10S to 113, inclusive, are held on the rod 116 in ordinal relationship relative to the outboard orders of the register wheels 23 by clips 118 and 119. The stirrup 117, as seen in FIGS. 3 and 7, is secured to the upper surface of the carriage bar 22 by suitable fasteners, such as screws 120. rl`he substantially horizontally disposed web of the stirrup 117 is constructed with a series of downwardly formed ears, at the forward edge thereof, providing a seat for a blocking, or safety plate, to be described later herein.

As seen in F1G. 8, each of the tens-transfer drum actuators 105 to 113, inclusive, is of such a length that it extends from one order into the adjacent higher order and becomes effective, following a rotation thereof by mechanism later to be described, to transmit an increment of rotation to a higher order register wheel as the adjacent lower register wheel passes from "9 to 0 during an additive operation, or passes from to 9 during a subtractive operation. Referring now to FiG. 9, it will be seen that each tens-transfer drum actuator comprises a main body portion, or cylinder, 124 in the form of pinion wire. On one end of the pinion wire cylinder 124, a circular end plate 125 is secured, having a portion thereof of a greater radius forming an arcuate actuating finger, or shoulder, 126. As seen in FIG. 4, the arcuate actuating fingers 126 are of equal length and the actuator drums 105 to 118, inclusive, are mounted on the rod 116 in a manner such that the actuating fingers 1.26 are equiangularly displaced relative to each other, forming a helix circumferentially about the rod 116. Thus, in the normally inactive position of the actuator drums 10S to 113, inclusive, a chordal edge 127 of each of the arcuate tens-transfer actuatingy fingers 126 is displaced an equiangular extent in a counter-clockwise direction (FlG. 4) from that of the adjacent lower order drum actuator. Therefore, it can be seen that upon rocking movement of the cylinders 124 in a clockwise direction (FIG. 4), by means to be described hereinafter, the leading, 0r chordal, edge 127 of the tens--transfer actuator finger 126 of a lower order tens-transfer actuator drum will enter into the notch 102 of the corresponding backing disk 101, followed successively by the entry of the actuator finger 126 of each higher order actuator drum into the notch 102 of its corresponding backing disk 101. The leading edge 127 of the finger 126 provided on the lowest order tens-transfer actuator drum 105 will require the least angular rotation to effect an entry into its corresponding notch 102, while that of the highest outboard order drum 113 will require the greatest degree of angular rotation to become engaged in its corresponding notch 102.

As explained above, the arcuately formed tens-transfer actuating fingers 126 (FIG. 4) of the tens-transfer drum actuators 105 to 113, inclusive, are of an equal length, which is sufiicient to permit the rotation of the highest ordinal tens-transfer actuating finger 126 into engagement with the notch 102 of the corresponding backing disk 101 without disengagement of the lowest ordinal actuating finger 126 from the notch of the corresponding backing disk 101. Also, if an outboard order register wheel has been rotated so that the notch 102 in the associated disk 101 is not in a position to receive the leading edge 127 of the actuating finger 126 associated with the corresponding tens-transfer drum actuator, and if the leading edge 127 of the actuating finger 126 of an adjacent lower order actuator drum is rocked into the notch 102 of the corresponding disk 101, the leading edge 127 of the actuating finger 126 of the higher order drum actuator will enter the interdental space between the teeth of the corresponding gear disk 100 and will contact the lower surface of the associated backing disk 101. Due to the angular displacement, approximately 12, between the leading edges 127 of the actuating fingers 126 of the adjacent tens-transfer drum actuators, the engagement of the leading edge 127 of the higher order tens-transfer actuating finger 126 with the lower surface of the corresponding backing disk 101, will prevent the active positioning of the actuating fingers 126 to the left thereof relative to the notch 102 or interdental spaces in the corresponding disks 1021 or gear disks 100, respectively.

Referring to FIGS. 4, 8 and 9, each of the tensatransfer actuator drums 105 to 11?., inclusive, carries an end plate 128 secured on the left end of the pinion wire cylinders 124. A laterally extended ear 129 is provided on each end plate 12S and, as seen in FIG. 4, the right-hand, or lowermost, edge of each ear 129 is equiangularly disposed from the trailing edge of the arcuately formed tenstransfer actuating finger 126 secured on the opposite end of each cylinder 124. inasmuch as the tens-transfer actuator drums are ordinally arranged on the rod 116 in accordance with the arrangement of the register wheels 23, the end plate 125 of a higher order actuator drum is positioned adjacent the end plate 120 of the adjacent lower order actuator drum and the laterally extended ear 129 of the end plate 12S overlies the trailing edge 130 of the actuating finger portion 126 of the adjacent end plate 125. Thus, it becomes apparent that upon rotation of a lower order tens-transfer actuator drum, clockwise if viewed from the left as in FEG. 4, all higher order tens-transfer drums will likewise be rotated, rotation of the lower order actuator drum being under the control of mechanism to be described hereinafter.

The normally inoperative position of the leading edge 127 of the actuating finger 126 associated with each tenstransfer actuator drum is schematically shown in FIG. 4. As a lower order cylinder 124- is rotated to move the leading edge 127 of the associated actuating nger 126 into the operative position relative to the corresponding backing disk 101 or gear disk 100, each of the cylinders 124 to the left thereof (FG. 8) will likewise be rotated. if each of the register wheels 23 from the twelfth to the twentieth order is standing at 0, as indicated by the angular position of the notch 102 in the associated disk 1151 (FiG. 8), the rotation of the lowest order tens-trans fer actuator drum 10S will effect entry of the associated actuating finger 126 into the corresponding notch 102. The rotation of the tens-transfer actuator drum 105 will also cause a similar rotation of the tens-transfer actuator drums 106 to 113, inclusive, to effect an entry seriatim of the respective associated actuating fingers 126 into the corresponding notches 102. However, should any one of these register wheels 23 be standing in a position other than the 0 position thereof, the leading edge 127 of the tens-transfer actuating finger 126 corresponding to that order register wheel will be rocked into the aligned interdental space between teeth of the associated gear disk 100, and each of the actuating fingers 126 to the left thereof will be precluded from entry into the respective corresponding notches 102 or gear disks 100.

1n order to effect a rotation of the tens-transfer actuator drums 10S to 113, inclusive, a plurality of driving gear sectors 146 to 14S, inclusive, is provided, one for each of the actuator drums. As seen in FIGS. 3 and 7, the driving gear sectors to 148, inclusive, are ordinally arranged in accordance with the ordinal arrangement of the tens-transfer actuator drums 105 to 113, inclusive,

,and are mounted for independent rocking movement on a shaft 149 so that the teeth of each gear sector are enmeshed with the teeth of the corresponding pinion wire cylinder 124. Shaft 149 extends longitudinally of the register carriage 20 axially parallel with the rod 116 and is supported at its ends for endwise movement in the depending fianges of the stirrup 117, similarly to rod 116. Each gear sector 1150 to 148, inclusive, is secured on a hub 150 which provides the pivotal support for the gear sectors on the shaft 1539. Each of similar sleeves 151 is positioned on the shaft 149 between adjacent gear sectors and serves to maintain the gear sectors in their ordinally spaced relationship. A lobe is provided on each gear sector 140 to 147, inclusive, adjacent the pivotal end thereof, and serves to control the rocking movement of the corresponding gear sector by means to be described hereinafter. A pair of clips 152 and 153 are employed 9 adjacent the respective ends of the shaft 149 to prevent any lateral sliding movement ofthe gear sectors on the shaft.

As explained above, a clockwise rotation of the lowest order tens-transfer actuator drum 105 (FIG. 4) to its operative position will effect a similar rotation of all higher order tens-'transfer actuator drums. Conversely, a counter-clockwise rotation of the highest order tenstransfer actuator drum 113 to its normally inoperative position will cause all lower order actuator drums to be restored to their inoperative position. For this purpose, a relatively strong spring 154 (PEG. 3) is secured at its one end to the forward carriage rail 25 and is supported at its 'other end on a pin 155 carried by the gear sector 14S` coacting with the highest order tens-transfer actuating drum 113. Spring 154 normally serves to bias the gear sector 148 in aV clockwise direction (FIG. 3) which will impart a counter-clockwise rotation to the corresponding actuator drum 113 and, therefore, all actuator drums to the right ythereof to a position determined by the engagement of the ear 129 of the tens-transfer actuator drum 165 with the lower edge of an inverted L-shaped limit stop 133 (FIG. 7). The limit stop 133 is secured tothe lower surface of the web portion of the stirrup 117 by any suitable means, such as screws 134, and is preferably formed of a thermoplastic material, having resilient properties to materially reduce the bouncing, or backlash, of the tens-transfer actuator drums upon their return to the normally inactive position thereof.

Referring to FIG. 8, the gear disk 100 and backing disk 101 associated with each of the register orders from the twelfth to the twentieth, inclusive, is shown with the notch 102 in each disk 101 in the 0 representative posi- `tion of the corresponding register wheels 23. 1t will be recalled that an incremental transfer into the twelfth, or highest, inboard order is under the control of a conventional tens-transfer mechanism. Therefore, following a rocking movement of the tens-transfer actuator drums 105 to 113, inclusive, by mechanism to be described, each actuating finger 126 will enter the corre.- sponding notch 102, with the carriage in the leftmost position shown in FIG. 7, and a tens-transfer of a subtractive sign character into the twelfth order register wheel 23 will effect an incremental clockwise rotation of the associated disk 101 (FIG. 8). Thus, shaft 116 and the tens-transfer actuator drums thereon will be translated to the left, thereby imparting a similar clockwise rotation to each of the higher order register wheels 23. If the twelfth to the twentieth order register wheels 23, inclusive, are standing at 9, the notch 192 in the associated disks 101 will be in al position one tooth-space clockwise from the position of the notches 162, as shown in FIG. 8. Assuming that an additive machine operation is initiated, the shaft 1.16 and tens-transfer actuator drums thereon are rst moved to the left in FIG. 8 to align the tens-transfer actuating fingers 126- with the notch 102 in the corresponding disks 1151. Subsequent to the -rocking of thev actuating fingers 126 into the corresponding notches 102, a tens-transfer of an additive sign character into the twelfth order register wheel 23 will cause a counter-clockwise increment of rotation of the wheel 23 and the associated disk' 161 will effect a movement of the shaft 116 and tens-transfer actuator drums to the right, thereby imparting an increment of rotation to each ofthe higher order register wheels.

As mentioned earlier, the rod 116 and shaft are movable axially to either of two positions, such movement being in accordance with the sign character of registrations in the register dials 23 during Veach 'machine operation. For the adjustment of the rod 116 and shaft 149, ka setting slide 160 is slidably supported, adjacent its ends, by similar pin-and-slot connections 161, 162 on the lower forward surface of the carriage frame bar 22. In 'cross-section, the form of the slide 16) is substantially that of an inverted channel on the outer surface of the web portion of which the horizontal leg of an L-shaped bracket 163 is secured. Movement of the slide in either direction imparts a similar translation to the rod 116 and shaft 149 and, for this purpose, the vertical leg of the L-shaped bracket 163 is disposed between the clip 11S and the highest order tens-transfer actuator drum 113, and between the clip 153 and the actuator drive sector 148 associated with the actuator drum 113, the rod 116 and shaft 149 passing through apertures in Ithe vertical leg of the bracket 163.

To control the lateral adjustment of the channel slide 160, one of the flanges thereof is mutilated to provide a plurality of ears, or lobes, 166 which are ordinally spaced in accordance with the spacing of the actuating fingers 126 of the respective tens-transfer actuator drums 10S to 113, inclusive. Onesuch car 166 is provided for each ordinal position of the shiftable carriage 2i), and when acted upon by a positioning mechanism, to be described hereinafter, becomes effective to selectively move the slide 160 to either the additive sign character control position or the subtractive sign character control position.

The slide 160 is resiliently retained in either of its two positions, i.e., the subtractive position shown in FIGS. 7 and 8, or the additive position to the left of that shown. For this purpose, a three-armed lever 169 is pivotally mounted on a stud 170 secured on the carriage frame bar 22. A bifurcation 16S in the lower end of the depending arm of three-armed lever 169 is engaged with a pin 167 secured on the slide 160 adjacent the left end thereof, so that upon movement of the slide 164) to the left or right (FIG. 7), the lever 169 is rocked clockwise or counter-clockwise, respectively. rEhe extent of rocking movement of the lever 169 is determined by the engagement of the free end of the upwardly extended arm of lever 169 with one or the other of limit stops 176 or 177 on carriage frame bar 2,2. The third. or laterally extending arm 171 of three-armed lever 169 carries a pin 172 having an annular groove therein in which one end loop of a toggle spring 173 is engaged. At its other end, a loop in the spring 173 is engaged in an annular groove of a pin 174, also secured on carriage frame bar 22. Thus, upon passage of the pin 172 below center, the spring assists in the movement of the slide 161) to the right and resiliently retainsl the slide in its moved position. Similarly, upon movement of the slide 1611 to the left (FIG. 7) to the additive position thereof, and upon passage of the pin 172 above center, the spring 173 assists in the movement of the slide and serves to resiliently retain the slide in its moved position.

As stated above, a positioning mechanism is provided for adjusting the setting slide 160 to either of its two adiusted positions in accordance with the sign character of a registration in the machine of the type presently being described herein. As explained hereinbefore, the sign character of `a registration in the inboard register wheels 23 is selectively controlled by an adiustment of the plus-minus gate 32. In addition to controlling the sign character of a registration into the inboard order wheels 23, the adiustment of the plus-minus gate 32 also serves to simultaneously effect a similar adjustment of the setting slide 166 to control the sign character of the registration of a transferred increment into the outboard order numeral wheels 23. The ordinally arranged ears 166 extend downwardly from the forward edge of the web Dor-tion of the channel slide parallel to the rearwardly disposed flange thereof (FIG. 3). Within the channel portion of the slide 160 the vertical offset end of an upstanding plus positioning ringer 181 is disposed, and the nger 181 is secured on an elongated hub 182 rockably and slidably mounted on a shaft 183 substantially below the slide 16d. Shaft 133 is positinned outwardly from, and parallel to, the left side frame 13 and is secured at its respective ends in brackets 184 and 186, each of which is secured by any suitable means, such as screws 18S and 187, respectively, on side frame 13. The upper end of the plus positioning finger 181 is provided with an ear ld, substantially at right angles to the vertical offset portion of the finger, for selectively cooperating with an adjacent positioned ear 166 of the setting slide 161i to move the slide 1611 to the left from the position shown in FIG. 7 to ythe additive position thereof. Similarly, the vertical offset end of a minus positioning linger 1.69, similar to the plus positioning finger 131, carries an ear 191, formed at a right angle thereto in opposition to the ear 13B of the finger 181, for selective cooperation with an adjacently positioned ear 166 of the slide 160. At its lower end, the minus positioning linger 189 is secured on a hub 199 suitably journalled for rocking movement on the reduced portion of the hub 182 of the plus positioning finger 131 and slidable therewith on the shaft 1&3. The vertical offset ends of the positioning fingers 181 and 189 are suitably spaced from each other to permit a scissorlike oscillation of the fingers and are normally positioned to either side of the plane of travel of the ears 166 on the slide 161i, thereby permitting ordinal shifting of the register carriage 29.

Upon initiation of a machine operation, the adjustment of the plus-minus gate 32 serves to actively position either the ear 183 of the plus positioning finger 181, or the ear 191 of the minus positioning nger 1559 relative to the adjacently positioned ear 166 of the slide 160, thereby enabling a subsequent adjustment of the slide 161) in accordance with the setting of the plus-minus gate 32. To control the active positioning of the plus finger 181 or minus finger 189, an arm 199 (FIG. 3) is secured on the plus-minus gate shaft 3d and is provided with a bifurcation 198 in the end thereof engaging a pin 197 secured on one arm of a bellcrank 194 pivoted on a stud 195 on side frame 13. The upper end of the vertically extended arm of the bellcrank 194 is formed at a right angle thereto and pivotally supports a resilient disk 1%, preferably composed of a rubber composition, positioned between the positioning fingers 181 and 139. Thus, it can 'oe seen that for an additive machine operation, a setting of the plus-minus gate 32 in a counterclockwise direction (FIG. 3) is effective to move the fingers 181 and 189 to the right so that the ear 188 of the finger 181 is actively positioned relative to they adjacent ear 16d (FiG. 7). 1n a like manner, a setting of the plus-minus gate 32 for a subtractive operation (clockwise in FlG. 3), the fingers 181 and 189 are moved to the left to actively position the ear 191 of the finger 189 relative to an adjacently positioned ear 166.

Referring now to FGS. 3 and 7, the setting slide 168 is shown in the subtractive adjusted position wherein a lateral movement of the fingers 131 and 189 (to the right in FIG. 3) will position the ear 18S of the plus positioning finger 181 for engagement with the adjacent ear 166 of the slide 111i). Similarly, if the previous operation was an additive operation, the slide 160 will remain in its additive adjusted position (to the left of the position shown in FIG. 7) and the adjacent ear 166 will be positioned for engagement by the ear 191 of the minus positioning finger 189 following a lateral movement of the fingers 131 and 139 (to the left in FIG. 3). A subsequent scissorlike oscillation of the fingers 131 and 159 will render either finger 181 operative to move the slide 1611 from the subtractive to the additive position, or finger 139 operative to move the slide from the additive to the subtractive position shown in FIG. 7.

Following the adjustment of the positioning fingers 181 and 189 for a single machine operation, or during the progress of a plural order operation, the oscillatory scissorlike motion of the fingers 181 and 189 is effected by a cyclically controlled mechanism. The adjustment of the setting slide 169 and its associated mechanisms, in accordance with the sign character of a registration in the inboard orders of the register, is required in order 12 that an incremental transfer into the outboard orders of the shiftable register carriage 21B may be accomplished. For example, should the register, or accumulator, wheels 23 show a value of 0 and a subtractive operation is initiated, the setting slide 169, tens transfer drum actuators to 113, inclusive, and the respective associated actuator drive sectors 1411 to 148, inclusive, must be set in their subtractive, or rightrnost, adjusted position (FIGS. 7 and 8) prior to the tens-transfer phase of the operation. Conversely, should the accumulator wheels 23 show a value of 9, then the setting slide 160, drum actuators 1115 to 113, inclusive, and the respective actuator drive sectors 146i to 148, inclusive, associated therewith, must be adjusted to their leftmost, or additive, position prior to the tens-transfer phase of the operation. For this purpose, one arm 295 (FIGS. 3 and 7) of a pius control bail 294 is rockably mounted on the shaft 1ST, while the other arm 2&8 thereof carries a hub journalled on the reduced intermediate portion of a hub 21d of a minus control bellcrank 215, also rockably mounted on the shaft 183. The arm 205 of bail 204 extends upwardly and is provided with an elongated stud 296 secured thereto and engaged in a vertically disposed slot 207 in the plus positioning finger 181. The other arm 2438 of the plus control bail 204 extends laterally through a stepped aperture 2fi9 in the left side plate 13 for cooperation with a roller 211 carried on an actuating disk 210 pinned on the leftmost, or sixth, actuator shaft do forwardly of the locking disk S6 (FIG. 2). Therefore, it becomes apparent that with each cyclic rotation of the disk 210, the roller 211 thereon will rock the arm 26d counter-clockwise (FIG. 7) so that an osciliation of the plus positioning finger 181 is effected.

To control the oscillation of the minus positioning finger 189, an upwardly extending arm 216 of the bellcrank 215 carries an elongated stud 217 engaged in vertically disposed slot 21S in the minus positioning finger 189. Each of the studs 206 and 217 is on a common radius but, in the normal position of the fingers 181 and 189, is angularly displaced one from the other. The other arm 219 of the bellcrank 215 extends laterally through the aperture 209 in the frame member 13 and is normally angularly displaced from arm 268 of bail 204 for cooperation with a roller 220 on disk 210. The respective arms 2118 and 219 lie in a plane adjacent the opposite sides of the disk 210 and normally rest against the hub of the disk extending beyond each side thereof. Arms 298 and 219 are resiliently maintained in engagement with the respective hub extensions of the disk 210 by means of a torsion spring 224 coiled counterclockwise (FIG. 7) about the hub 214 of bellcrank 215 between the bellcrank 215 and the arrn 2&8 of bail 204. One end of the torsion spring 224 overlies a pin 22.5 on arm 208 and its other end underlies a pin 226 on the arm 219. Rollers 211 and 220, respectively, are carried on either side of the disk 210 and are angularly displaced relative to each other, so that during the first part of each cycle of rotation of the flange 219, each of the rollers 211 and 22@ engages the respective arms 208 and 219 to effect a simultaneous oscillation of the plus and minus positioning fingers 181 and 189, respectively, in opposite directions. Thus, the torsion spring 224 normally operates to retain the ears 188 and 191 of the respective plus and minus positioning fingers 181 and 189 in arcual spaced relationship, whereby the setting slide may be adjusted during the tens-transfer phase of an operation, as Will be described hereinafter, to the position opposite that of its set position, even though one of the positioning fingers is in the active position relative to the ordinally active ear 166 of the setting slide.

Subsequent to the oscillation of the positioning fingers 181 and 189 for the selective adjustment of the setting slide 1d@ and the additive or subtractive positioning of the tens-transfer drum actuators 105 to 113, inclusive, relative to the corresponding tens-transfer disks 101,

13 means are brought into play to rock the one -actuator drive sector 140 to 147, inclusive, associated with the highest inboard order register wheel 23, to rock the corresponding tens-transfer drum actuator and each of the tens-transfer drum actuators to the left thereof.

As explained hereinbefore, each of the individual actuator drive sectors 140 to 147, inclusive, is provided with a lobe 165 for controlling the rocking movement of the respectively associated tens-,transfer drum actuators 105 to 112, inclusive. However, it `will be recalled that the relationship between a lower :order tens-transfer drum .actuator and the adjacent higher order drum actuator yis such that only a lower `order drum actuator need be rocked to effect a rocking movement of each of the drum actuators to the left thereof (FIG. 8*). In each ordinally shifted position of the register carriage 20, the lobe .165 of the actuator drive sector corresponding to the register Wheel 23 which has become the highest inboard order wheel, lies in a position to the right of the left side frame 13 (FIG. 7) for cooperation with a hook portion 164 in the free end-of a tens-transfer enabling arm 262. Arm 262 extends longitudinally of the Kmachine in .a substantially horizontal plane, and at its forward end, .an ear extends upwardly V,providing a pivotal mounting at 263 on the upper end vof an actuator lever 246 rockably lmounted on a shoulder screw 247 in side frame `13. The rearward, or hook, end 164 of the arm 262 is distended to project to the `right (FIG. for active engagement with the lobe 165 of the'actively positioned one of the actuating sectors 140 to 147, inclusive, operatively associated with the highest inboard order register' wheel 23. Also, the loop of the hook 164 of arm 262 .is sufficiently large to enable the movement of the lobes 165 of the actuating sectors therethrough, upon ordinal shifting movement of the carriage and with the parts in 4the normal condition shown in FIG. 3. There is no lobe 165 on the actuator drive sector 148 associated with the tens-transfer actuator drum 113 corresponding to the twentieth, or highest outboard, order register wheel 23, since, upon movement of the highest outboard order wheel into the position of the highest inboard order wheel, i.e., the extreme right-hand position of the carriage, no rllgpose would be served by the rocking of actuator drum Subsequent to the adjustment of the slide 160 to enable the registration of transferred increments into the outboard order register Wheels 23 of a like sign character to the registrations in the inboard order register wheels 23, actuator lever 246 is rocked, imparting a reciprocatory movement to the arm 262 whereby the hook end 164 thereof causes a rocking movement of the actively positioned actuating sector, thereby Vimparting an angular rotation to the associated tens-transfer drum actuator and each higher order drum actuator. Arm 262 is guided in its reciprocatory movement by the sliding engagement of the lowermost surface of the hook end 164 thereof With the vertically offset end portion of a bracket 266 (FIGS. 3 and 5) secured on the left side frame 13.

The reciprocation of the arm 262 (to the right in FIG. 3) to its active position and return, is under the control of a cam follower lever 252 and an associated cam 251. Lever 252 is pivotally mounted intermediate Aits ends on the shoulder screw 247 secured on frame plate 13 adjacent lever 246 and at its upper end carries an integrally formed L-shaped ear 254, the leading edge of the horizontal portion of which abuts the edge of lever 246. A relatively strong spring 255 is secured at its one end on an ear 256 extending laterally of lever 246 and at its other end is engaged in an aperture adjacent the end of the vertically disposed L-shaped ear 254 of lever 252, normally serving to maintain the abutment of the ear 254 with lever 246. At its lower offset end, the lever 252 carries a roller 2 53 which is retained in engagement with the periphery of the cam 251 under the tension of a spring 257 secured at its one end in lever 252 and supported at its other `end on a pin 25S on side frame 13. The cam 251 is secured on the outer end of the main drive shaft 50 which, it will be recalled, revolves once for each cycle of machine operation, including the ordinal shifting of the carriage 20. The configuration of the cam 251 is .such that after approximately 240 of each cyclic counter-clockwise rotation of the cam (FIG. 3), the roller 253 will ride upon the high part of the cam, thereby rocking lever 252 in a clockwise direction. This rocking of the lever 252 occurs subsequent to the adjustment of the sign character control slide 160 and prior to the termination of the digitation phase of the c cle.

yIn each additive or subtractive machine operation, the rocking of the lever 252 by the cam 251 is operative by means of spring 255 to rock lever 246 clockwise (FIG. 3), thereby causing arm 262 to actuate the ordinal actively positioned actuating sectors to 147, inclusive. There are, however, two conditions wherein the rocking of the lever 246 is prevented, upon rotation of cam 251, one such condition being that of a shifting operation of the carriage 20 and the other being that of an improper ordinal alignment of the carriage following a shifting operation thereof.

In the normal full-cycle position of the parts, or during a shifting operation of the carriage 20, lever 246 is blocked against rocking movement by the engagement of an ear 245 formed at a right angle to the lower extended portion of lever 246, with the lower surface of a square stud 244 secured on an upstanding arm 242 adjacent the free end thereof. During the overlying engagement of the square stud 244 with the ear 24.5 of lever 246 and the rotation of cam 251, lever 252 is rocked clockwise (FIG. 3)., yieldably stretching the spring 255. Arm 242 is pivotally mounted on a stud 243 secured on left side frame 13 and is rockable counter-clockwise or clockwise in accordance with the setting of the plus-minus gate 32 for an additive, or subtractive, machine operation, thereby moving the square stud 244 out of active engagement with the ear 245 on lever 246.

To control the disengagement of the square stud 244 with the ear 245, a link 241 is pivotally mounted at its one end on arm 242 and at its other end on the vertically extended offset end 232 of an arm 231 of a centralizer mechanism, generally indicated at 230 (FIGS. 3 and 6). Arm 231 is rockably mounted on the plus-minus gate shaft 34 and at its lower extended end carries a pair of opposed arms 233 and 234 adjacent thereto and pivotally supported thereon at 235 and 236, respectively. The pivotal connections 235 and 236 are equally radially disposed from the axis of the shaft 34 and the arms 233 and 234 normally extend upwardly therefrom with the upper end portions of the arms substantially parallel. At its upper end, each of the arms 233 and 234 is similarly formed angularly outwardly (FIG. 6) and is normally maintained in engagement with the respective parallel edges of the offset .portion of arm 231 by means of a relatively strong spring 237 supported at its ends between `similar ears on the respective arms 233 Iand 234. An

arm 240 is pinned on the plus-minus gate shaft 34, and the free end of the arm is formed at a right anglethereto for engagement at its extremity between the inner parallel edge surfaces of the upright arms 233 and 234. The formed-over end of the arm 240 is of a width equivalent to that of the upward extension of the arm 231 so that, in the normal condition of the parts, the spring 237 normally urges the inner edge of the upper end portion of each arm 233 and 234 into engagement with the respective edges of the formed-over end of the arm 240, thereby maintaining arms 232 and 242 centralized in the normally inactive centralized position of the plus-minus gate 32.

The plus-minus gate 32 is normally resiliently maintained in its inactive position by a well-known centralizer mechanism (not shown). However, upon counter-clockwise or clockwise rocking movement of shaft 34 (FIG. 3),

to engage either the plus gears 28 or minus gears 29 with the corresponding dial shaft gears 24, the plus positioning finger 131 or minus positioning finger 189 is actively positioned relative to the adjacent ear 166 of slide 160. Simultaneously therewith, the arm 240 serves, through arm 233 or arm 234 and spring 237, to rock arm 231, thereby moving the square stud 244 to one side or the other of the ear 245 on lever 246. Subsequent to the movement of the stud 244 from its normal position overlying the ear 245, the cam 251 becomes effective to rock levers 252 and 246, causing a reciprocation of the arm 262 and a rocking movement of the ordinally actively positioned actuator drum of the tens-transfer actuator drums 105 to 113, inclusive, and each actuator drum to the left thereof. If, for any reason, the plusminus gate 32 should be restored to its normally inactive position prior to the return of the lever 246 to its normal position, the stud 244 will engage one side or the other of the ear 245 and the spring 237 will yield temporarily, or until the lever 246 is restored to the position shown in FIG. 3, whereupon the tensioned spring 237 will cause the stud 244 to restore to its normal position overlying the ear 245.

As stated above, operation of the actuator arm 262 is prevented when, following a shifting operation of the carriage 20, the inboard order register wheels 23 vare not properly aligned with the corresponding orders in the keyboard. For this purpose, a boss, or raised portion, 267 (FIGS. 3 and 5) is provided on the upper surface of the actuator arm 262 forwardly of the hook end 164. A blocking plate 260 extends longitudinally f the left end portion of the carriage 20 and is preferably secured thereon between the front guide rail 25and the flange of the stirrup 117 by screws 270. A series of ordinally arranged notches 268 is provided in the lower edge of the blocking plate 269, one such notch corresponding to the highest inboard order, with the carriage in its leftmost position, and one corresponding to each higher outboard order, with the exception of the highest order. Upon proper registry of the inboard order register wheel gears 24 with the corresponding plus-minus spools 30, in any shifted position of the carriage, the notch 263 corresponding to the highest inboard order Will be aligned with the boss 267. The size of the notches 268 is sufficient only to permit the passage of the boss 267 therethrough, so that if the register wheel gears 24 are out of registry with the corresponding spools 30, the boss 267 will engage the face of the plate 269, upon actuation of the lever 252 by cam 251, and spring 255 will yield. Yielding of the spring 255 will also be effected when the carriage is in its rightmost position, since there is not notch 268 provided for the highest outboard order. Thus, a rocking movement of the drive sectors 140 to 147, inclusive, actively positioned for control by the actuator arm 262, will be precluded.

Upon shifting movement of the carriage 20, to the right from the position shown in FIG. 7, each of the outboard order register Wheels 23 is ordinally shifted inboard of the machine and thereafter cornes under the control of the conventional tens-transfer mechanism. It is, therefore, necessary that actuation of each tens-transfer drum actuator 105 to 112, inclusive, be prevented as corresponding register Wheel 23 is ordinally shifted to the right and becomes the next to the highest inboard order. For this purpose, a blocking arm 274 is spaced from, and is secured on, the left side frame 13, having its free end formed at a right angle to the frame plate 13 extending laterally parallel to the plane of shifting movement of the lobes 165 of the actuator drive sectors 140 to 147, inclusive. The positioning of the laterally extended portion of the arm 274 is such that, as the carriage 20 is ordinally shifted to the right (FIG. 7) and as each register wheel 23 becomes the next to the highest inboard order wheel, the lobe 165 of the corresponding rive sector .140 to 147, inclusive, moves into engagement with the rearward face of the extended portion of the arm. Thereafter, any rocking of the blocked drive sector and associated drum actuator is precluded and, because of the overlapping arrangement of the ear 129 of a lower order drum actuator with the trailing edge of the adjacent higher order drum actuator, each drum actuator to the right of the positively blocked drum actuator is also disabled.

It will be recalled that the conventional tens-transfer mechanism is operable to be eective up to, and including, the register wheel 23 occupying the position of the twelfth, or highest inboard, order of the machine. Upon initiation of a subtractive machine operation, the sign character setting slide 160 will be adjusted to the subtractive position (FIG. 7) if displaced therefrom. Now, assuming the condition wherein the register carriage 20 occupies its leftmost position (FIGS. 1 and 7) and the accumulator wheels register 0, the arcuately formed actuating finger 126 of each tens-transfer actuator drum 105 to 113, inclusive, will be aligned with the notch 102 (FIG. 8) in its respective corresponding disk 101. After approximately 240 of the subtractive cycle, the cam 251 becomes effective, through lever 252 and spring 255, to rock lever 246 (FIG. 3), thereby moving arm 262 to the right, rocking the actively positioned drive sector 140. Upon rocking movement of the sector 140, the chordal edge 127 of the associated finger 126 of the associated tens-transfer actuator drum 105 is rocked into the aligned notch 102 in the corresponding disk 101, followed seriatim by the entry of the actuating finger 126 of each higher order actuator drum into the aligned notch 102 of the respective corresponding disks 101.

Due to its configuration, the cam 251 serves to retain the actuating fingers 126 in engagement with the aligned notches 102 of the corresponding disks 101 until near the end of the cycle of operation. During the digitation phase of the operation, the subtraction of 1 in any keyboard order of the machine will cause the correlated register wheel 23 to be rotated from 0 to 9, thereby initiating the tens-transfer phase of the operation. The conventional tens-transfer mechanism is effective thereafter to cause a tens-transfer successively into each higher order register wheel 23, including the twelfth order wheel.

Heretofore in machines of the type described, the tenstransfer operation was interrupted with the tens-transfer into the twelfth order register wheel 23. However, in the use of the auxiliary tens-transfer mechanism described herein, the tens-transfer will be carried into the highest order register wheel 23. As the twelfth order register wheel passes from 0 to 9, the disk 101 associated therewith causes a lateral translation of the tens-transfer drum actuators 105 to 113, inclusive, actuator drive sectors to 148, inclusive, and setting slide 160 to the left (FIG. 7), thereby effecting a simultaneous incremental rotation of the outboard order numeral wheels 23 from 0 to 9. The slide 160 will be resiliently retained in the left-hand adjusted position by toggle spring 173. It will be recalled that the left-hand position of the slide is the additive position thereof, so that if the following machine operation is of an additive sign character, the plus positioning finger 181 will only be idly rocked. However, if the next machine operation is to be a subtractive operation, the rocking of the minus positioning finger 189 will move the setting slide 160, and the mechanisms associated therewith, to the subtractive position thereof. Similarly, if the setting slide 160 is left in the subtractive adjusted position shown in FIG. 7 and the ensuing machine operation is an additive operation, the plus positioning finger 181 will become effective to move the slide 160 to its left-hand position.

As another example of the operation of the auxiliary tens-transfer mechanism, assume the condition wherein the accumulator carriage 20 and the setting slide 160 are positioned as shown in FIG. 7, and the sixteenth order numeral wheel 23, i.e., the fourth outboard order wheel, registers a value other than 0. Following the initiation of a subtractive operation, the arcuately formed actuating finger 126 of each of the tens-transfer drum actuators 105 to 10S, inclusive, will be rocked into the aligned notch 102. in the corresponding backing disks 101 of the associated wheels 23, whereas the leading edge 127 of the actuating finger 126 of the drum actuator 109 will enter the aligned interdental spacev of the gear disk 10G associated with the sixteenth order numeral wheel 23. inasmuchas the leading edges 127 of the actuating fingers 126 form a helix circumferentially about the rod 116 and because of the inter-relationship of adjacent drum actuators, the entry of the finger 126 of the drum actuator 109 into the interdental space of the corresponding gear disk 100 prevents the active positioning of the actuating finger 126 of each higher ordinal drum actuator 110 to 113, inclusive. Consequently, as the highest inboard order numeral wheel 23, i.e. the twelfth order wheel, passes from to 9 upon the subtraction of 1, the thirteenth, fourteenth and fifteenth order wheels 23 will be simultaneously rotated to register 9, while the registration in the sixteenth order wheel 2.3 will be decreased by 1. it becomes apparent, therefore, that if, during a subtractive operation, the highest inboard order numeral wheel 23 or any of the higher outboard order numeral wheels 23 register a value other than 0, the actuating finger 126 of the corresponding tenstransfer drum actuator will enter the aligned interdental space of the gear disk 19t? associated with this particular register wheel, while the actuating fingers 126 to the left thereof will remain inactive. Similarly, during an additive operation and upon the engagement of an actuating finger 126 in an interdental space of the corresponding gear disk ttl@ associated with the highest order numeral wheel 23 registering a value other than 9, the actuating fingers 126 to the left thereof will remain inactive.

While the salient features of the invention have been described in detail with respect to one embodiment, it will, of course, be appreciated that numerous modifications may be made within the spirit and scope of the invention, and it is, therefore, not desired to limit the invention to the exact detail shown, except insofar as they may be defined in the following claims.

What is claimed is:

l. In a calculating machine having a frame,'a carriage mounted for endwise shifting movement ordinally from one end position to the other end position on said frame, a plurality of ordinally arranged register wheels journalled in said carriage, certain of said register wheels lying inboard of said frame and others lying outboard thereof when said carriage is in the left end position, means settable to control the sign character of registrations in said certain of said register wheels, a main tens-transfer mechanism arranged within said frame operable to execute an incremental transfer into said certain of said register wheels, and a cyclically operable actuating means therefor: an auxiliary tens-transfer mechanism mounted on said carriage for shifting movement therewith rendered operable by said main tens-transfer mechanism to effect an incremental transfer into said other of said ordinal register wheels comprising the combination of a series of auxiliary tens-transfer gear disks, one correlated to the highest order register wheel of said certain of said register wheels and one correlated to each of said other of said register wheels, each of said auxiliary tens-transfer gear disks having a tens-transfer notch therein representative of the 0 registering position of the associated register wheel, a rod supported on said carriage for endwise adjustment to either of two positions in accordance with the sign character of a registration in said certain of said register wheels, a plurality of tens-transfer actuating cylinv drical racks ordinally disposed relative to said other of said wheels and adjacently mounted for rockable and nonslidable movement on said rod for adjustment therewith, each of said tens-transfer actuating cylindrical racks including a first portion and a second portion, said first portion of a cylindrical rack corresponding to a lower order register wheel being cooperatively related to the said second portion of a cylindrical rack corresponding to the adjacent higher order register wheel whereby a rocking movement of the lower order cylindrical rack effects a rocking movement of the adjacent higher order cylindrical rack, a shoulder on the said second portion of each of said cylindrical racks angularly displaced relative to each other forming a helix circumferentially about said rod and operable upon adjustment of said rod for engagement in the said notch of the corresponding one of said gear disks upon rocking of the associated cylindrical rack, a plurality of actuating gear sectors ordinally arranged for cooperation with said cylindrical racks and independently operable to cause a rocking movement of the associated tens-transfer cylindrical rack, a shaft supported on said carriage for endwise movement conjointly with said rod and having said actuating gear sectors adjacently mounted for roekable and non-slidable movement the'eon, means positionable by said settable means for selectively adjusting said rod and said shaft to either of the said two positions. a drive means operated bv said cyclically operable actuating means for controlling the operation of said positionable means subsequent to the positioning thereof by said settable means, means normally operable to bias said actuating gear sectors to an inoperative position in either adjusted position of said shaft, a tens-transfer enabling means operable to rock a predetermined one of said normally inoperative actuating gear sectors to operative position in timed relation to the operation of said main tenstransfer mechanism thereby engaging each of said shoulders of a predetermined one of said tens-transfer actuating cylindrical racks and all higher order cylindrical racks successively with the said notches of the corresponding ones of said tens-transfer gear disks tomechanically continue a tens-transfer operation into said other of said register wheels upon operation of the main tens-transfer mechanism and an incremental transfer into the highest order register wheel of said certain of said wheels, means mounted on said carriage for shifting movement therewith operable to prevent operation of said enabling means when said carriage is in either the right end position or intermediate the ordinally shifted positions thereof, and means for preventing the rocking movement of said cylindrical racks as the corresponding wheels are moved inboard of said frame upon shifting movement of said register carriage toward an end position thereof.

2. In a calculating machine as defined in claim l comprising also means normally operative to prevent operation of said tens-transfer enabling means rendered ineffective by the operation of said settable means.

3. In a calculating machine having a register. a plurality of ordinally arranged numeral wheels journalled in said register, means settable to control the sign character of registrations in said numeral wheels, a cyclically operable actuating means, and a tens-transfer mechanism, the combination comprising a rod supported in said register for endwise adjustment to either of two positions in accordance with the sign character of a registration in said numeral wheels, means controlled by said settable means for adjusting said rod', a plurality of cylindrical racks ordinally disposed relative to said numeral wheels and adjacently mounted for rockable and nonslidable movement on said rod for adjustment therewith, each of said cylindrical racks including a first portion and a sec ond portion, said first portion of each cylindrical rack being cooperatively related to said second portion of each adjacent lower order cylindrical rack, whereby a rocking movement of the lower order cylindrical rack effects a rocking movement of the adjacent higher order cylindrical rack, a shoulder formed on said first portion of each of said cylindrical racks angularly displaced relative to each other forming a helix circumferentially about said rod, a plurality of ten-tooth gear disks associated with said numeral wheels, one for each of said numerals wheels, each of said gear disks having a notch in the periphery thereof representative of a or 9 registration in the associated numeral wheel and adapted for engagement by the said shoulder on said first portion of the corresponding cylindrical rack in accordance with the adjustment of said rod, a series of gear means ordinally arranged for cooperation with said cylindrical racks and selectively operable to rock the cylindrical racks effecting engagement seriatim of the said shoulder on the said rst portion of each of said racks with the notches in the corresponding gear disks, a shaft supported in said register for endwise movement conjointly with said rod and having said gear means adjacently mounted for rockable and nonslidable movement thereon, and a power-operated tens-transfer enabling means operable to rock a predetermined one of said gear means in timed relation to the operation of said machine thereby rocking the corresponding cylindrical rack and each higher order rack to effect engagement of the associated ones of said shoulders with the notches in the corresponding gear disks to enable an incremental rotation of each higher order numeral wheel upon passage of a lower order numeral wheel from 0 to 9 or 9 to 0 in accordance with the sign character of a registration in said register.

4. In a calculating machine having a frame, a car riage mounted for endwise shifting movement from one end position to the other end position on said frame, a plurality of ordinally arranged register wheels journalled in said carriage, certain of said register wheels lying inboard of said frame and other of said wheels lying outboard thereof when said carriage is in the left end position, means settable to control the sign character of registrations in said register wheels, and a main tens-transfer mechanism situated within said frame operable to control an incremental transfer into the said certain of said register wheels: an auxiliary tens-transfer mechanism mounted in said carriage for effecting a tens-transfer in the other of said register wheels comprising the combination of a rod supported on said carriage for axial adjustment to either of two positions, a plurality of cylindrical racks rockably mounted on said rod and ordinally arranged relative to said other of said register wheels, overlapping means on each lower order cylindrical rack whereby rocking movement thereof is operable to effect a rocking movement of the adjacent higher order cylindrical rack, a shaft on said carriage, a plurality of tenstransfer drive members ordinally arranged on said shaft relative to said cylindrical racks, each of said tens-transfer drive members being operable independently to cause the rocking movement of the corresponding one of said tens-transfer actuating members and each higher order actuating member, means positionable by said settable means to selectively adjust said rod to either of said two positions, a tens-transfer gear associated with each of said other register wheels, a backing disk coupled to each of said auxiliary tens-transfer gears, each of said backing disks having a notch therein representative of the 0 position of the associated register wheel and adapted for engagement by the corresponding cylindrical rack upon rocking movement thereof during a subtractive or additive operation when the said register wheel is in the 0 or 9 position, respectively, and a powerdriven means operable to rock a predetermined one of said tens-transfer drive members in each ordinally shifted 20 position of said carriage and in timed relation to the operation of said main tens-transfer mechanism whereby a tens-transfer operation is continued into said other of said register wheels upon operation of the main tenstransfer mechanism and incremental transfer into the highest inboard order register wheel.

5. In a calculating machine having a frame, a carriage mounted for endwise shifting movement ordinally from one end position to the other end position on said frame, a plurality of ordinally arranged register wheels journalled in said carriage, certain of said register wheels lying inboard of said frame and the other of said wheels lying outboard thereof when said carriage is in the left end position, means settable to control the sign character of registrations in said register wheels, a main tens-transfer mechanism within said frame operable to effect an incremental transfer into said certain of said Wheels, and a cyclically operable actuating means: an auxiliary tenstransfer mechanism mounted on said carriage operable to effect an incremental transfer into said other of said register Wheels upon operation of said main tens-transfer mechanism comprising the combination of a rod supported in said carriage adjacent said other of said wheels for endwise adjustment to either of two positions in accordance with the sign character of registrations in said register Wheels, a plurality of ordinally arranged cylindrical gear members roclcably mounted on said rod and adjustable therewith, a first portion of each gear member having a cooperative relationship with a second portion of the adjacent higher order gear member whereby a rocking movement of a gear member effects a rocking movement of the yadjacent higher order gear member, a shaft supported on said carriage, a plurality of tenstransfer drive members ordinally arranged on said shaft relative to said gear members and independently operable to effect a rocking movement of the corresponding gear member and each higher order gear member, means positionable by said settable means to enable the selective adjustment of said rod to either of the said two positions, means driven by said cyclically operable actuating means for controlling the operation of said positionable means subsequent to the positioning thereof by said settable means, means normally biasing said drive members and said gear members to an inoperative position in either adjusted position of said rod and said shaft, an auxiliary tens-transfer wheel associated with the highest order register wheel of said certain of said register wheels and each of said other of said register wheels, a backing disk on each of said auxiliary tens-transfer wheels, each of said backing disks having a notch therein operable in the 0 or "9 registering position of the associated register wheel to be engaged by the coordinal gear member upon rocking movement thereof by the corresponding one of said drive members subsequent to the subtractive or additive adjustment, respectively, of said rod, and a power means for operating said tens-transfer drive members selectively in timed relation to the operation of said main tens-transfer mechanism to mechanically continue an incremental transfer from the highest order register wheel of said certain of said wheels into said other of said register wheels.

References Cited in the file of this patent UNlTED STATES PATENTS 2,089,770 Suter et al. Aug, lO, 1937 2,229,889 Friden Ian. 28, 1941 2,403,069 Friden et al. July 2, 1946 UNITED STATES PATENT OFFICE CERTIFICATE 0F CORRECTION Patent No. 3,022,948 February 27, 1962 Arthur J. Malavazos et alo It is hereby certified that error appears( in the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

Column 10, line 8, after "through" insert suitable line 15, for "car" read ear column 11, line 5, for "adjacent" read adjacently column 12, line 36, after "in" insert a Signed and sealed this 26th day of March 1963o (SEAL) Attest:

ESTON G. JOHNSON DAVID L LADD Attesting Officer Commissioner of Patents 

